Air conditioning system



July 26, 1949. w. w. PAGET 2.471.525

AIR CONDITIONING SYSTEM Filed Aug. 31, 1943 11 Sheets-Sheet 1 July 26, 1949. w. w. F'Acsla'r 2.477.525

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Patented July 26, 1949 2,477,525 AIR CGNDITIONING SYSTEM Win W. Paget,

Pennsyl Michigan City, Joy Manufaeturlng Company,

vania Ind.. assigner to a corporation oi' Application August 3l, 1943, Serial No. 500,877

(CI. ils-1.5)

6 Claims.

cabins or other passenger compartments of aircraft which are adapted to be operatedat widely varying altitudes.

It is imperative for high altitude iiight that the cabins or passenger compartments of aircraft be pressurized. It is permissible that the pressure in the cabin be allowed to follow substantially the variations in external pressure until a predetermined height is reached, for example 8,000 feet. If the elevation of flight is increased rapidly 'it is preferable not to allow the cabin pressure to reduce as rapidly as the reduction in external pressure occurs. From the elevation of 8,000 feet until a considerably greater height is reached, say 35,000 feet, it is desirable that the pressure in the cabin be maintained relatively constant at approximately the pressure which corresponds to 8,000 feet. It |is further desirable that if the plane have occasion to go above the upper limit mentioned, there shall be a variation in the cabin pressure with the changes in altitude so that the cabin pressure may again be reduced as the external pressure becomes lower-where when the plane goes abov pressure will be progressively reduced with higher elevations, and, for example, the same difference between cabin and external pressure which prevailed at 35,000 feet will be maintained through lowering of the cabin pressure. This capacity is very important both because it reduces the danger of damage to the cabin through excessive pressure differential between the inside and the outside thereof. and it also relieves the load on the pressurizing means which has to raise the pressure of the very rarened atmosphere to cabin pressure and which must work very hard at such extreme heights unless the cabin pressure can be further reduced.

For pressurizing means it is desirable to provide pumping means which shall have a large displacement in small compass and which shall be able actually to compress the air taken in through one or more compressions prior to clis-` say 35,000 feet the cabincharge: to provide pumping means which atV many altitudes shall avoid the consumption of unnecessary power and the needless generation of heat by operating as, or substantially as, a mere air displacement device, to provide pumping means whose speed of operation shall be automatically varied in accordance with predetermined changes in engine speed: to provide pumping means which shall automatically change its racteristics from a simple air displacement apparatus to a true compressor when certain conditions obtain, such as. for example, the ele vation of the apparatus to a height where the external pressure falls below a predetermined value: and to provide pumping means control oi speed is possible.

In order to maintain the desired pressures in the cabin there may be employed a pressure rematically communication between the interior ot the cabin and the atmospher said valve mechanism providing free communication. except when the plane increases its altitude of ilight too rapidly, beteween the interior higher altitudes.

To obtain desired temperatures within the cabin there is desirably provided suitable heat transfer equipment through which the air passes from the pumping means to the cabin. Since the air delivered to the cabin at high altitudes means when the latter may be stopped due to some fault of its driving means, there may be provided suitable check valves in the supply line.

An object of my invention is to provide animproved system for pressurizing the cabin o! an airplane. Another object of my invention is to provide an improved system for maintaining automatically suitable pressure conditions in the cabin of an airplane during flight at widely varying heights. Still another object of my invention is to provide an improved cabin pressurizing system having means for supplying air continuously to the cabin, and means for controlling the venting of the cabin so as to obtain the de sired pressures in the latter. Yet another object of my invention is to provide an improved system for producing the desired pressure and temperature conditions in the cabin of an airplane during Hight of the latter at widely varying heights. said system including means for supplying air continuously to the cabin. heat transfer means for regulating the temperature of the air supplied, and valve means for controlling the venting of the cabin to atmosphere.

In the accompanying drawings in which a preierred embodiment shown for purposes of illustration:

Fig. 1 is a diagrammatic view showing my improved pressurizing system arranged for use with a plane of the bi-motored type.

Fig. 2 is an enlarged side elevational view of one of the motor driven superchargers shown in Fig. 1.

Fig. 3 is an end elevation of the apparatus of Fig. 2, viewed from the left-hand end of Fig. 2 and showing the drive end of the apparatus.

Fig -i is an opposite end elevation of the apparatus shown in Fig. 2, being an illustration of the righthand end thereof.

Fis. 5 is an enlarged central vertical section on the plane of the line Fis. 3.

Fig. 6 is an enlarged horizontal fragmentary sectional view on the plane of the line B--i of Fig. 4, showing a detail of the hydraulic system.

Fig. 'l is a horizontal longitudinal sectional view on the planes of the line 1-1 of Fig. 5, with parts shown in elevation.

Fig. 8 is a view showing portions of the unloading mechanism shown in Fig. 'I in different positions and with certain additional parts shown in elevation.

Fig. 9 is a vertical sectional view on the plane of the line 8-3 of Fig. "l, with parts shown in full.

Fig. 10 is a vertical transverse sectional view on the plane of the line I-iil of Fig. 1, showing a detail of construction of the unloading mechanism.

Fig. l1 is an enlarged fragmentary sectional view showing venting means for the unloading valve operating cylinder. the view being taken substantially on the plane f the line iI--il oi.'

longitudinal -5 of Fig. 12 is an enlarged horizontal sectional view through the control mechanism at the right-hand end of the apparatus, the view being taken on the same plane as Fig. '1.

Fig. 13 is a fragmentary vertical transverse section on the plane of the line it-il of Fig. 12, showing a manually operable control valve positionabie to vary the speed of drive of the pumping apparatus.

Fig. 14 is a section Fig. 13.

Fig. 15 is an enlarged detail sectional view on the axis of the speed-responsive device for controlling the speed of drive of the apparatus.

Fig. 18 is a transverse vertical sectional view taken on the plane of the line i6-i8 of Fig. 15.

Fig. 17 is a fragmentary view generally similar to Fig. 15 but with parts shown in elevation and illustrating a different position of the parts.

Fig. 13 is a detail longitudinal sectional view on the plane of the line i8-I8 of Fig. 16.

Fig. 19 is a fragmentary detail view showing a locking screw for the governor.

Fig. 20 is an enlarged horizontal sectional view on the same plane as Fig. 7. showing details of construction of the external pressure-responsive unloader valve controlling pilot me Fig. .11 is a fragmentary view on the same plane as Fig. 20, showing the parts in different relative positions.

Fig. 22 is an enlarged transverse vertical secon the lines ll-Il of tion on the plane of the 'line 22-22 of Fig.

Fig. 23 is a longitudinal view on the line 23-23 of Fig. 22.

Fig. 24 is an enlarged fragmentary sectional view on the plane of Fig. 5, showing details of the speed-controlling drive clutch.

Fig. 25, is a vertical sectional view on the plane of the line 25-25 of Fig. 5, showing a portion of the driving gearing.

Fig. 26 is an enlarged transverse fragmentary sectional view showing a detail of the drive mechanism.

Fig. 27 is a fragmentary section on the plane of the line 21-21 of Fig. 26, showing a detail of a roller ratchet.

Fig. 28 is a section on the line 23-23 of Fig. 26. showing another detail of the roller ratchet mechanism.

Fig. 29 is a vertical sectional view on the plane of the line 29-23 of Fig. '1, showing the high pressure head of the pump.

Fig. 30 is a vertical transverse section on the plane of the line 33-30 of Fig. 5.

Fig. 31 is a sectional view taken on the planes of the line 3l-3i of Fig. 7. showing the intake end of the supercharger.

Fig. 32 is an enlarged horizontal sectional view of one of the check valves shown in the air supply line in Fig. 1.

Fig. 33 is an enlarged perspective view of one of the aftercoolers shown in the air supply line in Fig. 1.

Fig. 34 is an elevational view of the left-hand end of the controlling mechanism shown in Fig. 35.

Fig. 35 is a central longitudinal sectional view on the plane of the line 35-35 of Fig. 34.

Fig. 36 is a fragmentary sectional view on the plane of the line 36-36 of Fig. 34.

Fig. 3'? is an enlarged view of a portion of the pilot mechanisms shown in Fig. 35.

Fig. 38 is an enlarged view of another portion of the apparatus shown in Fig. 35.

Fig. 39 is a transverse section on the plane of the line 33-39 of Fig. 38, showing a detail of the control apparatus.

Fig. 40 is a sectional view on the same plane as Fig. 39, looking in the opposite direction.

Fig. 41 is a transverse section on the plane of the line Il-H of Fig. 35, showing a portion of the cabin pressure adjusting mechanism.

Fig 42 is a transverse section on the plane of the line t2- 42 oi Fig. 35.

Fig. 43 is a transverse sectional view on the plane of the line 43-43 of Fig. 35.

Fig. 44 is a transverse section on the piane of the line Il-M of Fig. 35.

Fig. 45 is a transverse section on the the line 45-45 of Fig. 35.

Fig. 46 is a transverse section on the plane of the line 46-46 ci' Fig. 35.

Fig. 47 is an enlarged longitudinal sectional .view through the vent control valve mechanism shown in Fig. 1.

Fig. 48 is a sectional View taken on the plane of the line 48-48 of Fig. 47, with portions broken away to facilitate illustration.

Fig. 49 is a fragmentary perspective view showing a portion of the ie-icing mechanism for the valve mechanism shown in Fig. 47.

Referring to the drawings. e'id tlrst to Fig. 1. it will he noted that the pres. `rlzing system is shown including two supercha zers i, i. connected by shafts 2, I in driven relation with plane of separate motors 3,3 of a bi-motored plane. It will be understood, of course, that the pressurizing system may include one or more superchargers, depending on the volume of the space to be pressurized, and that the superchargers may be driven by the same motor, if desired. Air is supplied to the superchargers under pressure during flight of the plane, through intake connections 4,4 opening to atmosphere through the leading edges of the wings of the plane. The superchargers discharge the air through aftercoolers 5, 5 to connections 6, 6 communicating with a common conduitI 8 past check valves Il. I0. The conduit B extends along the lower edges of the windows at the forward end of the cabin I2, and is provided with elongated ports I3, I3 opening into the cabin adjacent the windows so that air supplied to the cabin will pass close to the windows and aid in defrosting the latter. Arranged at the rear side of each of the aftercoolers is aap I5 for controlling the now of air over the aftercooler. Suitable means I5 are provided for adjusting the flap I5 in accordance with temperature conditions within the cabin, the flap being adjusted to increase the iow of air over the aftercooler as the cabin temperature increases so as to cause a greater cooling of the air supplied to the cabin. Arranged within the cabin is a valve mechanism I1 for controlling communication between the interior of the cabin and the surrounding atomsphere. The valve mechanism I1 is subjected to different pressures through a conduit I8 under the control of a pilot mechanism generally designated 20, described hereinafter more in detail. The pilot mechanism is connected through a conduit 2l with an atmospheric vent 22 opening through a wall of the cabin. A tank 23 is connected by a conduit 24 with the pilot mechanism 2l), and the rate of change of pressure Within the tank is restricted, as will be later explained.

Air pumping mechanism Each of the superchargers comprises a main casing part 3I and a pair of coasting rotors 32 and 33. The rotor 32 is a male rotor and comprises four helically arranged lobes 34, the rearward sides 35 of which are shown as generated curves in profile, while the leading or pressure side 35 of each of these lobes is, in profile, substantially in the form of a circular arc. The female rotor 33 is provided, in the form shown, with six helically arranged grooves 31 each adapted to cooperate with the lobes of the rotor 32, and the leading concave surfaces 38 of the groove 31 are in profile substantially in the shape of an arc to coact with the arcuate pressure surfaces 36 of the lobes of the rotor 32, while the following concave surfaces-39 of the grooves 31 are generated curves in profile. It will be understood that with a rotor of this character, a materially shortened sealing line ls had for the pockets or working spaces which are formed by the coaction of the rotors with each other. A different form of rotor construction may be used without departing from various aspects of my invention, as for example a construction in which the rotors have their respective lobes and grooves formed with generated surfaces in a well known manner. With such rotors, it will be evident that they will have, as it were, low pressure and high pressure ends.

In either case, the rotors are adapted to operate with space packing; that is to say, they are main- 6 tained in such relation to each other, through gearing, that there is no actual contact between the rotors with each other. Each of the rotors 32, 33 is herein shown supported at its ends by stub shafts, the rotor 32 having a stub shaft 43 at its low pressure end and a stub shaft 4l at its high pressure end; while the rotor 33 has a stub shaft 42 at its low pressure end and a stub shaft 43 at its high pressure end. I'he stub shafts 4l and 42 are supported in suitable bearing sleeves or bushings 44 and 45 supported in bores 45, 41 in an integral end casing portion 48 formed in one piece. as herein shown, with the housing 3l. A separate, plural-part head 50 supports ball thrust bearings 5l and 52 in which thestubshafts 4I and 43 are respectively mounted. These bearings position the rotors so that no contact can take place between them and the ends of the casing. The casing 3l is provided with an intake chamber 53 with which an intake passage 54 provided with suitable strainer, or other devices not shown for preventing the ingress of harmful material, communicates. and the intake space communicates with the righthand, low pressure ends of the rotors, and also for a substantial part of the length `of the rotors communicates with the back portions thereof soto-speak, the portions at the opposite side of the plane which includes the rotor axes, from the discharge. 'Ihe intake chamber 53 also includes curved recesses 53' extending substantial distanoes arcuately, the extent of these recesses being such that, in the illustrative embodiment shown, the intake chamber and its component recesses 53' provide intake communication with the rotor chambers over arcs of considerably more than The extent of the intake port, from the functional aspect, is, with the proportions shown, such that the "trailing" edges of the grooves 31 and of the spaces between the lobes 34 pass out of register with the intake port just before engagement or the start of compression within the tooth grooves and spaces begins. It will be evident, however, that a small amount of overlapping. so-to-speak, would be possible and to depend on the dynamic effect of the incoming air to oiset the tendency toward a reversal of flow caused by the initial compression. The casing 3| is provided with a discharge chamber 55 at the left-hand (high pressure) end of the rotors, and another chamber 55, whose purpose will later be described, communicates with the chamber 55 though it is separated therefrom for a substantial distance by a web 51. The discharge chamber communicates with the high pressure ends of the rotor chambers. as shown in Fig. 29.

For the purpose of maintaining the rotors out of contact with each other they are connected by interrneshing helical gears 53 and 5I, the gear 53 being splined, as at 62, to the stub shaft 4I, and the gear 5I being splined, as at 53, to the stub shaft 43. The gears 50 and 6I are so formed that their helix angles correspond in hand and lead to the helix angles of the rotors to which they are respectively fixed. Regardless of the speed at which the rotors turn, these gears operate to maintain the space packing heretofore referred to; in other words, a very small clearance between the surfaces of the lobes and the sides and bottoms ci the grooves of the rotors is maintained, thus preventing wear and permitting the operation of the pump at a speed far exceeding any permissible with rotors running in contact with each other. By reason of the smallness of the ananas clearance maintained and the high speeds of rotation, serious leakage ls prevented.

A drive shaft 10, preferably driven through a flexible non-back-lash drive such as, for example, that disclosed in my application Serial No. 443,414, flied May 18, 1942, is arranged in alinelent with the stub shaft 43 and has a driving connection therewith as shown at 1|. The drive shaft is journaled by means of a ball bearing I2 carried by the plural-part head 50 and engaging a cylindrical portion 13 on the drive shaft. Its other end is rotatably supported as later described. Surrounding a cylindrical hub portion 19 of the gear 8| is a bearing sleeve 80. and a cylindrical'portion 8| at the right-hand end of the drive shaft 10 rotatably surrounds the bearing sleeve and is journaled thereon. Keyed to the periphery of the cylindrical portion 8| of the drive shaft is a member 02 having a number of recesses 83 formed therein receiving rollers 8l which are operative, as later described, at times to effect a clutching between the member 82 and a cylindrically bored liner ring 88 keyed, as at 01, to the gear 6|. The recesses 83 have, as shown in Fig. 26, relatively straight base surfaces 80 and radial surfaces 0|. Through the latter surfaces there project spring-pressed plungers 82 adapted to act upon the rollers 84 and cause them to connect the members 82 and 88 upon predetermined relative rotation between the latter members. Springs 03 act against cross pins 94 and move the plungers 82 against the rollers 84. The pins are supported in end closure or plate members 91 and 88, and the rollers have stems 88 loosely received in openings |00 in the plates `81 and 98. These plates 91 and 80 are supported to turn with the member 82. It will be evident, referring to Figs. 25 and 26, that if the member 82 be driven counterclockwise it will, through the rollers 8l, be connected to the liner ring 86 and through the latter drive the gear I, and by virtue of the connection of gear 8| to shaft 43 drive the rotor 38, while through the meshing of gear 6| with gear 80 and the mounting of gear 80 on shaft 4|, rotor 32 will also be driven. If the gear 6| be driven counterclockwise at a greater angular rate than the member 82, it will not be connected to that member and may turn freely in the direction mentioned, relative to it.

It will be noted (Fig. 5) that the stub shaft 4| has another shaft |02 connected with it by means of a splined connector element |03 which has an axial bore |04 for reasons later explained. The left-hand end of shaft |02, as viewed in Fig. 5, is journaled in a ball bearing |06 carried by the plural-part head 50, and carries a gear |01 somewhat smaller than the gear 80. A gear |00. somewhat larger than the gear il, meshes with the gear |01 and is journaled by a ball bearing ||0 on a cylindrical portion |I| of the drive shaft 10. It also has a sleeve portion II2, internally spllned at ||3 and supported bv a ball bearing lil on a further cylindrical portion ||5 of the drive shaft 10. Discs ||1 connected. as shown in Fig. 24, to the sleeve portion ||2 are interleaved with other discs I|8 connected by splines il! to the drive shaft 10, which has a flange |20 adjacent the bearing lll serving as an abutment for the end one of the interleaved series of discs II1, ||8 when these are pressed together to connect the gear |08 to the drive shaft 10. 'A follower member |22 is slidably supported on a packing ring |23 mounted on the shaft and has an annular outer sleeve portion |24 with whose bore a peripherally packed plate |25 coacts to form a chamber |28 for clutch applying hydraulic pressure. A ring |21 seated in an internal groove in the sleeve portion |2I provides an abutment for a flexed annular spring |28 whose opposite side presses upon the side of the plate |25, and the spring |28 normally maintains the follower member |22 in clutch unloading position.

It may now be noted that when the clutch is loaded, the gear |08 will be connected directly to the shaft 10 and will drive the gear |01 and so the gears and 8|, and thus the rotors 22 and 28; and because the gear 0| will then be rotated faster than the member 22, and in the same direction with the latter, there will simply be an overrunnng clutch action and no tendency for connection between gear 8| and member 82.

It will be evident from what has been said that the drive shaft 10 is rotated counterclockwise in Fig. 3 and that the rotor 38 turns clockwise in Fig. 30 while the rotor 22 turns counterclockwise in the same figure, and that air taken in through the intake connection 5I is entrapped between the casing and the rotors and is progressively moved, and if it remains entrapped, compressed as it is moved to the discharge connection 55.

The compressor has automatic means for effecting Change in the manner (and accordingly in the speed) of drive thereof governed by a speed responsive device and it has automatic means for effecting the initiation of compressive action thereby governed by the pressure of the air surrounding the airplane. Both of these automatic means are hydraulically operated. so. having described the hydraulic clutch operating means which effects high speed drive of the compressor, I shall briefly describe the hydraulically controlled means for initiating compressive action, and then describe the hydrauic system and its controls which effect the operation of the clutch and the unloading means.

Referring particularly now to Figs. '1, 29, 30 and 31, it will be observed that the casing 3| at the intake side does not t at all closely to the peripheries of the rotors, and that there are, as previously described, arcuate intake grooves 53' which extend at the intake end of the pump somewhat more than in one case and somewhat less than 90 in the other past the plane which includes the axes of rotation of the rotors, but that there are wall portions respectively marked |32 and |33 which except for clearance adequate to constitute space packing do conform or fit quite closely to the cylinders traced by the outermost portions of the rotors and that these portions |32 and |33 intersect along a line |3I parallel to the rotor axes. Now, the fluid which is sealed in the successive progressively diminishing chambers between the rotors and the casing walls would be substantially compressed if no escape or discharge were provided between the times pairs of tooth spaces or grooves move out of communication with the grooves 53 and the instant that the leading edges of the tooth spaces come into communication with the discharge 55; and under certain conditions such compression is very desirable. But under other circumstances it is better to avoid material compression and thus conserve power and avoid unnecessary heating of the cabin. Accordingly, I have provided an opening at |35 so related to the length of the casing and the helix angle of the rotors that when the opening |25 is unobstructed no compression of the :duid enclosed between the rotors 32 and 33 will take place before communication with the opening |36 is had; and the relationship of the opening |65 to the discharge e 66 is such that the air remaining in the pockets in the rotors as these pockets move out of communication with the openings |35 will not be compressed before these same pockets communicate with the discharge 66. It may thus be noted that the position of the ends of the intake grooves 63' and the position and dimensions o! the opening |36 are such that with the helix angles of the rotors used, tooth pockets whose trailing" edges are just ceasing to communicate with the intake are Just about to commerce to have their forward edges pass over the opening |35; and that as the trailing edges of tooth pockets approach their points of final communication with the opening |65 when the latter is open they have their leading edges pass beyond the edge of the ilnal discharge opening, whereby there is displacement, but not compression, of fluid when the opening |35 is not closed by the valve |36, However, when valve |36 is closed, there is a substantial compression o! the fluid between the time the tooth spaces cease to communicate with the grooves 53' and move into communication with the discharge 66.

To control the opening |65, which has a peripheral wall which lies in the surface of a. cone, I have provided a valve I 56 whose shape is such that when the same is closed it conforms very closely to the walls |32 and |66, as may be seen in Fig. 10. This valve has ears |61 through which pins |36 pass, and these pins are secured in the arms or flanges |66 carried upon a. pivotal support member |66 which is secured, by a pivot pin |6I, to the wall of the casing 3|. A shoulder |62 on the valve and a shoulder |63 on the casing limit the closing movement of the valve |36 to a. position in which the walls of said valve conform exactly to the surfaces of the rotor chambers. This valve is adapted normally to be maintained open by a spring |65 engaging at one end the wall of a member |66 which forms a portion of the enclosure of the discharge chamber 56 and which is secured, in any suitable manner, to the casing 3|. The other end of the spring acts against a piston |61 having a packing |66 tting the walls oi' a cylindrical chamber |66 which is formed in a cylinderproviding member |56 also secured, in any suitable manner, to the casing 3| in a position overlying the member |66. A piston rod or operating stem |52 with an elongated eye |53 is connected at its outer end to the piston I 61, and by means of the eye and a pin |56 is connected to the valve |66. The piston |61 and the member |66 cooperate in forming a servo-motor |65 to which iluid may be admitted through a connection or passage |56 under a control hereinafter described, and a leakage port |56. shown in Fig. l1, is provided to conduct any liquid which may escape past the packing |66 to an oil sump |66 in the lower part of the casing 3|. When the servo-motor |55 is not under pressure delivered through the passage |56, the valve |66 may be moved to the open position shown in Fig. 8 by the spring |65, and in that inclined position it will otler very little obstruction to the discharge of iluid to the chamber 56 and thence to the interior of the cabin through any appropriate connection. When, however. pressure is supplied under certain predetermined conditions to the servo-motor |55, the piston |61 will be caused,

l0 through the Operating stem |62 and the pin |66, to close the valve |36, and the'compressor will then operate substantially precisely as though there were no opening III available. Thus depending upon the position or the valve ill, there is provided by the single unit in eect a mere displacement pump and a compressor capable taken in. That a dei-mite compression.

As previously indicated, the change in speed of operation of the compressor and the loading There is provided in the base of the casing Il the sump |66. This sump is disposed between the lower wall of the rotor housing and an outer wall |6| forming an integral part of the casing 3|. 'Ihe chamber is, in the horizontal position of the compressor, substantially horizontal, and a pump oi' the intermeshing gear tioned at the right-hand end oi' the casing as the same is viewed in Fig. 5, so that it is partially submerged and so that lsubmerged (in the casing) in the oil designated |62, includes a casing |66 having intersecting rotor chambers |66 therein, Fig, 22, in which are rotors |66 having interxneshing teeth |66 arranged at a slight angle to elements of the cylindrical surface in which the outermost points in the rotor teeth ile. An intake passage |61 conducts oil to the lower sides oi' the rotors |65. and the oil is carried around by the teeth |66 and is discharged to a discharge space 66 above the plane of the mesh line of the rotors |66. One oi' the rotors |66 drives the other, and the ilrst mentioned rotor is provided with a shaft |66 which extends through a ported cover plate |16 and carries a gear |1| which is in turn driven by a pinion i12 rotatablv supported on a sleeve member |13 later more fully described. A larger gear |16 is herein shown as formed inteerally with the gear |12. and the gear |16 is driven by a pinion |16 formed integral with the stub shaft 62 and arranged at the extreme righthand end of the latter in Fig. 5. A clean-out plug |16 is arranged below the oil pump in the bottom of the sump. The discharge passage |66 communicates with passages |16 in the cover |16. and |16 in a supplemental cover. and opens into the bore |66 of the sleeve member |13 previously mentioned. From the bore |66 the iiuid is discharged through branch passages |6|. Fie. 6. into a chamber |62 containing a strainer structure |63. Between the ends of the chamber |62 and suitably associated with the strainer is an annular peripheral member having a Peripheral groove |66 to which the strained lubricant obtains access through radial ports |65. The annular groove |66 communicates with a passage |66 which opens into an annular groove |61 surrounding the bearing bushing 65. The opposite side of the annular groove |61 opens into a passage I 66 whose upper end opens into a chamber |66. The chamber i 66 constitutes a distribution point for oil for lubricating purposes and for operating the speed-changing clutch mechanism previously described and also for fluid for closing the valve |66 previously mentioned. In line with the passage |66 there is another passage |66 opening outwardly and upwardly from the ll chamber |00. This communicates with an annular groove |02 in the bushing 00. The an- .nular groove has continuously in communication with it obliquely disposed passages |03 opening into a chamber in the stub shaft 00. The chamber |00 is connected by a. tube |80 suitably centered as at |00 within the rotor 02, and at the left-hand margin of Fig. 5 the tube |00 opens into a chamber |01 in the stub shaft 0|. As will be apparent from what has been previously described, the chamber |01 communicotes through the passage |00 with a hollow interior |00 of the shaft |02 and discharges through the left-hand end of the latter, as shown in Fig. 0. into a chamber |09 formed in the multipart head structure 00. Fluid is delivered from the chamber |00 through a lubricant tube 20| into a chamber between the rotor casing and the chamber |00 and which forms an enclosure for the motor driving gear earlier described. The lubricant tube 200 has two discharge orifices 202 and 200 which respectively discharge lubricant onto the peripheral surfaces oi' the gear couples |01, |00 and 00, 0|, thereby keeping the gear couples 00, 0| and |01, |00 adequately lubricated. The lubricant, after its discharge over these gears, passes downwardly within the chamber 20| and is conducted out of the casing through a passage 200 and a tube 200 of small diameter opening through the side wall of a larger tube 201 back into the sump |00. Lubricant is also discharged directly through the tube 201 back into the sump |00. The prence oi' the branch tube 200 of small diameter prevents all of the lubricant in thesuxnp |00 from flowing into the chamber 20| when the airplane has occasion to make a dive. A drain plug 200 is arranged in a position to permit the draining oi lubricant from the chamber 20|.

It will be noted that in the stub shaft 00 there is, at the right-hand end of the chamber |00, a partition 2| 0 to the right of which there is a valve-receiving bore 2| Obliquely extending es 2|2 connect the annular groove |02 with the bore 2|| at points near the partition 2|0, and a further annular passage 2|2 formed in the bushing 00 is connected with the interior of the bore 2|| by radial passages 2|0. suitably supported on the rear end of the stub shaft 00 is a mmmting 2|0 for a speed-responsive governor 2|0 which serves in conjunction with a spring 2|1 housed in the interior oi' a valve member 2 I0. to vary the position oi' that valve member in the bore 2li. The valve member will be observed to be open from end to end, as at 220, and to house the spring 2|1 within it in such a manner that the spring acts on the right-hand end of the valve in Fig. 15 at one end and at its other end acts on the partition or wall 2I0. The valve has a left-hand end collar 222', another annular peripheral collar 222 spaced by a groove 220 from the collar 222 and a further enlarged collar-righthand portion 220- spaced by a peripheral groove 220 of substantial length from the collar 222. The support member 2|! has a portion 221 guidingly engaging the portion 220 and is traversed by openings 220 so that in in certain positions of the valve 2|0 there may be a discharge into a chamber 200 at the right-hand end of the compressor, o! fluid entering the chamber 2| i through the radial passages 2|0.

The governor 2|0 includes ily weights 202 pivotally supported on tranverse pins 222 in earlike portions 200 carried by the support 2 0. Portions 220 of the ily weights at the opposite side of the l2 pivots thereof from the main m of said fb weights carry adjustable screw devices 220 which have heads 221 adapted to engage the right-hand end surface of the valve 2|0, and upon the attainment of the shaft 00 to a predetermined speed of rotation the ily weights actuate the portions 220 to move the valve 2|0 to shift the valve from the position shown in Fig. i5 to that shown in Fig. i'l, thereby allowing fluid entering the bore 2|| through the radial passages 2li to be vented while at the same time preventing any delivery of fluid from the pump to the radial passages 2|0. The cutting oil' oi' the supply of fluid to the radial passages 2|0. and the venting of fluid from these passages through the bore 2|| will effect, as shortly described, a reduction in the speed of the rotors. This reduction in speed,

` however, will not be sufficient to effect an opera- Kil) tion of the speed governor permitting the valve to move again to a position for supplying duid to the passages 2|0. as the design of the governor is such that it becomes operative to force the valve 2|0 to the left only upon the attainment of a speed as of the order of '|000 R. P. M.. while after once assuming the position oi' Fig. 17 a falling oil of the speed to a. lower speed oi' the order of 4000 R. P. M. will be necessary before the weights will be moved in and permit the reestabiishment of iiuid delivery to the chamber |20 of the hydraulically operated clutch mechanism.

The circumferential groove 2|2 is connected below the stub shaft 00 with a passage 20| which extends downwardly parallel to the axis of the passage |00 and opens through an opening 202 into the interior of the bore of a valve-receiving bushing 202. This valve-receiving bushing contains a rotatable valve 200, which is used primarily for testing purposes and which has an operating handle 200 by means of which the valve may be turned into any one of three different positions. In the position of the valve 200, shown in Fig. 5 and in Fig. 12, a diametric passage 200 connects the opening 202 with an opposite opening 201 in the valve sleeve and via the latter opening to the passage 200 which is connected through a port 200 in the bearing sleeve 05 and an annular groove 200 and radial passages 25| with a chamber 202 within the interior of the stub shaft 02. The outer end of this chamber 202 is closed by a plug 202, while the other end of the chamber 202 is connected by a suitably centered tube 200 with arrangements for effecting the operation of the clutch mechanism previously described and i'or the performance of certain lubricating functions. Before proceeding with the description oi this mechanism, it may be pointed out that the valve 2|0 at speeds of the rotor 22 below a predetermined number of R. P. M. will be in the position shown in Figs. 5 and 15 and will connect the pump discharge through the ports and passages previously described with the tube 200, but that at speeds above such a predetermined number of R. P. M. the valve 2|0 will assume the position shown in Fig. 1'1 and cut 0R communication completely between the passages |00 and 20| and to vent 20| back to the sump through the chamber 200. Now it will be observed, referring particularly to Figs. 5 and 24 that at the left-hand end of the tube 200 there is a heli or funnel shaped member 201 fitting a bore 200 of the stub shaft 02, and that a split spring ring 200 operates to prevent possible movement of the member 201 out oi' the bore in the stub shaft if any loosening should occur.

15 Within a stepped bore 200 Within the drive shaft 18 there is arranged a hollow plunger member 26| which is provided at one end with Va per-l forated flange 262 adapted to seat against a split ring 288 secured within the inner wall o! the drive shaft 18. The plunger member 26| is engaged by a spring 284 which reacts against a shoulder 286 within the drive shaft. and a thimble 288 closes the left-hand end of the chamber within which the element 28| is movable. The interior of the chamber communicates, through obliquely radially extending passages 281, with the outside of the drive shaft between the ball bearings 12 and H8. Other radially obliquely extending passages 268 connect the interior of the stepped bore 288 at the right-hand end of the plunger member 26| in communication with the chamber |26.

The mode of operation of the mechanism which has just been described is as follows: When the compressor is started, a driving connection is immediately established between the shaft 18 and the gear 8|, and the pump |82 commences to deliver fluid through the strainer, through the passage |86, the chamber |89, the passage |88, the oblique passages 2|2, the annular groove 224, the radial passages 2|4, passages 24|, 246, 248, 25| and the tubular conduit 255 to the interior of the member 251 and to the space between that member and the plunger member 26|. The fluid immediately passes through the perforations in the flange 282 and through the radial passages 268 into the chamber |28 and brings the clutch discs ||1 and ||8 into contact with each other. As the oil continues to flow through the tube 255, the member 26| moves to the left compressing the spring 254, and the compression of this spring is so determined that the clutch pressure will be gradually applied as the member 26| moves to the left. When this member reaches its extreme lefthand position, the clutch discs may be rmly pressed against each other and drive of the rod tors at the higher speed, when the gear |88 is the driving element, will be effected. It will be appreciated that this high speed driving will be continued until the speed of the compressor builds up to such a degree that the valve 2|8 will be shifted by the governor, and then the slower speed drive between the shaft 18 and the compressor will be initiated. It will be noted that lubricant will be supplied from the space between the member 28| and the member 251 to the splines.

The manually operable valve 244 previously mentioned can be adjusted as previously described to such a position as to restore high speed drive of the compressor after such high speed drive has been automatically interrupted, or to prevent interruption of high speed drive upon the attainment of the predetermined speed of operation at which a shift to low speed drive is normally effected. Furthermore, in another position of adjustment, this valve may be so operated as to preclude the high speed drive completely. It will be noted that in addition to the diametric passage 246 formed in the valve there is a longitudinal peripheral passage 218, Fig. 14, which opens into the space 21| at the righthand side of the valve, a space which is connected by a passage 212 (Fig. with the chamber 288 which communicates with the sump. When the valve 244 is turned to bring the passage 218 into communication with the passage 24B and to blank off the port 242 with the cylindrical portion of the valve opposite the groove 218, it will be evidently impossible to transmit pressure through the tube 268 for effecting high speed drive of the compressor. The valve 284 also has an opposltely extending longitudinal peripheral groove 214 opening through its end which forms a portion of the bounding wall of the chamber |88. When the valve is turned so as to bring the passage 214 into communication with the passage 248, fluid will be supplied from the chamber |88 continuously to the passage 248 and the tube 285 and high speed drive of the compressor will alone be possible. Referring to Figs. 4 and 5 it will be apparent that means is provided for locking the handle 248 of the valve 244 either in midposition where the drive of the compressor is controlled by its speed automatically by the speed governor or in either of the other two positions mentioned.

The chamber |89 has a laterally extending passage 216 (Fig. 12) communicating with the same. This passage is adapted to be connected by a longitudinally extending passage 211 under the control of a spring loaded valve 218 with a passage 219 opening into an annular chamber 288 which surrounds the sleeve 248 and which is connected at its opposite side with a passage 28|. The function of the spring loaded valve 218 is to maintain a suillcient pressure in the chamber |89 under all circumstances when the compressor is running to insure the operation of the speed change mechanism. The passage 28| has a bore 282 communicating with it, and a valve 288 reciprocates in the bore. A side vent 284 opens out of the bore and leads into the space 288, and a spring 285 having an adjustable follower 286 is adapted to control the pressure in the passage 288. The passage 28| communicates through a port 288 with a bore 289 of a valve seat member 288 mounted in a passage 29| which is connected by another passage 292 to the passage |56 leading to the chamber |55 to which fluid is supplied to actuate the valve |86. It will be evident that if through escape from the bore 288 is prevented fluid will be supplied to the servo-motor |55 at a pressure determined by the valve 288 and that again, subject to the same condition, the valve |88 would be closed whenever the pump |62 was being driven. However, means is provided whereby the pressure is vented freely from the bore 289 back to the sump at all times when the airplane is operating at levels where the external pressure is below a predetermined amount. It will be observed that thevalve seat member 298 is provided with a pluralityr of ports 284 (Figs. 12, 20 and 21) opening through a surface surrounded by an annular valve seat 285 and that there is further provided a central guide extension 296. Reciprocably mounted upon this guide extension is a valve element 281. The movement of this valve element in an opening direction is limited by a sleeve portion 288 formed on a threaded sleeve member 299 which is supported in a further sleeve mounting element 888 carried by a wall of the casing 8|. An adjustable closure element and spring tension regulator 88| engages a spring 882 which acts upon the valve 291 and normally tends to seat it. Connected to the valve 281 and to the sleeve member 288 at opposite sides of the sleeve portion 288 are bellows devices 888 and 884 bounding a chamber 885 in which the sleeve 288 is enclosed, and this sleeve is perforated so that free communication may at all times exist throughout the interior of this chamber. The

l chamber 966 is evacuated, and the compression of the spring 902 is so determined that until the pressure acting upon the exterior of the bellows arrangement falls to a predetermined low value, the valve 291 will be held firmly open against the stop sleeve 299. When, however, the pressure in the casing 996 falls below a predetermined .value, the valve 291 will promptly seat and interrupt the discharge of iiuid back to the sump and cause the building up oi.' such a pressure in the chamber |56 as to close the valve |96 and cause the compressor to operate as a compressor instead of a displacement means. It will be noted that the walls of the casing 966 are perforated as at 909, 9||i to permit the fluid passing through the passages 294 to tlow freely to the sump through the chamber 299. The chamber 299 is connected to external pressure-pressure outside the cabinthrough a pressure device of any suitable construction as shown at 9|| (Figs. 4 and 7), and a similar device, 9|I' (Fig. 9), connects the chamber 29| to atmosphere. The setting of the spring 992 is such that the valve 291 is normally open at heights of the airplane below 25,000 feet. The valve 291 is of the overbalanced type, being of the sharp opening variety, so that when the valve |99 is to open, it may be permitted to open sharply and cleanly. Extending axially through the guide extension 296 is a passage 9|2 through which fluid passes from the bore 299 to the interiors of the .sleeve member 299 and the bellows device 964. When the valve 291 is seated, iluid supplied under pressure through the passage 9|2 acts against the outer end oi' the valve and counteracts the increase in pressure on the inner end oi' the valve produced by the fluid acting through the ports 294.

It will be noted that the rotor 99 is hollow from end to end and that passages 9|9, 9|4 connect the space surrounding the left-hand stub shafts 4|, 49 with the interior of the rotor, while passages 9|5 extend through the stub shaft 42, so that any tendency of lubricant to enter the rotor spaces is prevented by pressure equalization. The casing 9| has cooling fins 9|6.

An extended summary oi' the mode oi operation of the illustrative embodiment oi the invention which has now been described in detail is not necessary in view of the explanations given of the modes of operation oi' the component parts. It may be noted, however, that when the airplane takes off each compressor will have its valve |95 open and will simply move large quantities of air at take-oil conditions into the cabin. When each compressor is caused to rotate, it will be started initially at the slower speed, drive being from the drive shaft 1|| through the automatic roller clutch mechanism to the gear 6|, As soon as. the compressor has operated long enough to produce the necessary oil pressure in the system-a thing which occurs almost instantly-the high speed drive of the compressor rotors will be initiated unless the manual control valve 244 should have been moved to prevent thisan unlikely condition as this valve is used mainly for test purposes. Ob-

viously, if a substantial period of idling is de 16 the high speed drive by interrupting the supply of clutch loading pressure to the friction clutch loading member |22. Thus yduring the relatively high speed operation of the compressor during flight the low speed drive will be in operation. The nature oi the governor is such as to avoid hunting, and when the speed of the compressor is brought up to a value suillcient to initiate low speed drive there will be required a greater reduction in speed than will be occasioned by the change from one drive to the other before the compressor will again shift back to the high speed drive. Ii the airplane rises to the requisite height so that compression of the air instead oi displacement thereof is necessary for satisfactory operation, the evacuated diaphragm will permit the closing of the valve 291 and there will be fluid supplied to the piston |41 o! the servo-motor |55, and the valve |96 will be closed and the compressor will then operate to compress the iluid, and all of the fluid taken in will be discharged through the regular discharge passage 55. It will be evident that the compressor will be adequately lubricated at all times and that a pump of the character shown has such capacity for the moving of lubricant that a very eiiective delivery of lubricant to the points requiring lubrication will be assured.

Air supply system Air discharged from the supercharger is conducted through a connection 929, Fig. 33, to the interior of a funnel shaped member 92| where it enters a series of laterally spaced tubes 923 of the aftercooler 5. The tubes are supported in spaced relation by plates 924 so as to provide spaces through which air may pass from a propeller of the plane transversely o ver the tubes. As the air discharges from the tubes it enters a funnel shaped member 925 connected in communication with the connection 6. As shown in Fig. 32, the connection 6 is connected in communication with a passage forming portion 921 of the check valve i9. The portion 921 opens into a chamber 929 which communicates, at a point spaced laterally of the passage portion, with the conduit B. Arranged within the chamber 92a is a valve member 929 urged continuously by a spring 99|) toward the inner end 0I the portion 921 for closing the latter and preventing an escape of air from the chamber 929 toward the supercharger.

Cabin. vent valve mechanism The valve mechanism I1, as shown in Figs. i and 47, is supported by a wall 99|| of the airplane cabin over an opening 99|. Connected to the cabin wall surrounding the opening 99| are reinforcing rings 992 and 999, and attached to the ring 999, as by bolts 994, is an annular member 996 bent to form an annular V-shaped groove 996. A Z-shaped annular member 999 and a valve casing 999 are connected, as by bolts 949, to the inner edge of the annular member 935. Surrounding the member 99B is a coiled spring 94| bearing against the inner flange portion of the member 999 and against an annular valve member 942 which seats on the member 995 at opposite sides of the groove 996 for controlling communication between the interior of the cabin and the surrounding atmosphere through ports 949 in the member 995. The valve casing 999 has a discharge orifice 944 communicating with atmosphere through the inner opening of the annular member 995. A valve seat of fibre or 17 other mutable material is provided at 345; and a generally annularly arranged discharge passage 343, partially cut up into sectors by supporting anges 341. is surrounded by a screen 343 which serves to prevent the possibility of any objects from within the cabin obtaining access into the interior of the valve mechanism and thereby interiering with its operation. Cooperating with the valve seat is a vent valve 353 which is relatively conical at its outer end and is provided with a cylindrical portion 35| at its inner end. The vent valve is of the approximately balanced type, and is traversed by openings 352 so that the pressure at its opposite sides may be equalized. The valve is mounted ln any suitable manner, herein by means of a nut and shoulder arrangement 353 at the outer end of an operating stem 354 which is guided in bushings 335 supported in a sleeve-shaped member 353 attached to a wall 331 of the valve casing. The casing 333 carries a housing portion 353 supporting a cover member 353. An expansible chamber device 363 is enclosed within the housing portion 353 and comprises a bellows 33| secured at one end in sealed relation by studs 362 and an annular end element 333, with the housing portion 353 and the cover member 359; and the other end of the bellows is connected to a head 365 comprising a ring member 366 and a conical portion 331 formed integral with the stem 354. The conduit I3 is connected at 333 within an opening in the cover member 353. Openings 363 connect the interior of the casing 3'53 with cabin pressure. When the cabin pressure materially exceeds the pressure within the bellows 36|, the valve 353 will be opened. When the pressure within the bellows is the same as cabin pressure, the valve 353 will be closed.

Secured to the cylindrical portion 35| of the valve 353 is a ring 313 guided on the outer wall of a cylindrical portion 31| of the valve casing. Projecting outwardly from the portion 35| are pins 312 extending through slots 313 in a surrounding wall portion 314 of the casing. Between the valve portion 35| and the wall portion 314 there is rotatably mounted a cylindrical member 315 having a radial flange 311 to which there is welded an upstanding operating ilanged portion 313 carrying a button or finger piece 313. The

18 ot its steepness can be used to cause the valve w reciprocate rapidly and thus to free it from ice.

Thepilot, controlling calce mechanism The pilot mechanism 23 comprises, Fig. 35. a casing 433 having a head 43| secured thereto m any appropriate manner. The head 43| has a boss 432 in which the connection I3, at its end remote trom the cabin vent valve mechanism l1 is mounted, and a further boss 433 in which the conduit 2| leading to the exterior of the cabin, is appropriately mounted. It also includes a central boss 434 in which there is a mounting 43| for securing in leak-tight relation with respect to a chamber 433 formed in a plug member 431 the end of the conduit 24 which is remote trom the tank 23. The plug 431 is threadedly connected within the central portion of the head 43|. The joint between the head 43| and the casing 433 is a gasketed one, as indicated at 433. The casing 433 is provided at a point near its longitudinal center with suitable supporting means, herein shown as arms 4| l. for supporting a centrally arranged body 4|2 within whose interior certain valve mechanism is arranged. The body 4 l2 is traversed by a longitudinally extending bore 4|3 into which, from the opposite ends thereof, there extend plug members respectively numbered 4|4 and 4|4'. Each of the plug members 4|4 and 4|4' is traversed at its outer portion with a bore 4|5 opening into a central chamber 4I3, and each of the plug members has a smaller opening 4|1 alined with the opening 4I5 and opening into a space 4|3 between the plug members. The space 4|3 will be observed, in the construction shown, to be bounded peripherally by the wall of an annular groove 4I3 formed in the body 4|2 and by the end surfaces of the plug members 4|4 and 4|4'. Each of the chambers 4|6 is connected by radial passages 423 with an annular groove formed in the body 4 2, the annular groove associated with the plug member 4|4 being designated 42| and the annular groove associated with the plug member 4|4' being designated 42 The grooves 42| and 42| are connected by oblique passages 422 and 422' respectively with a bore l 423 of a conduit 424, which may be a brass pipe member 315 is traversed, as shown in Fig. 49,

by a series of openings each including a relatively right triangular portion 333 and a communicating helically extending elongated portion 33|. The inner wall 332 of the portion 333 lies in a plane perpendicular to the axis of the mechanism. The walls 334 and 335 of the helically extending portion 33| extend obliquely outward. The outer wall of the portion 333 is relatively sharply inwardly inclined, as at 333. The bottom wall of the portion 333 is horizontal, as at 331. Now it will be evident that by turning the member 315 counterclockwise, in terms of directions looking down upon the valve device in Fig. 47, and causing the helically disposed portions 33| to engage the pins 312, the valve 353 may be adjusted to and held in substantially any desired portion. It will further be observed that when the member 315 is left in the position indicated in Fig. 41, the valve may move freely back and forth without interference from this member. It will also be evident that when the valve is nearly closed, if the same becomes stuck by ice or the like, the surface 333 may be caused to wedge in the valve and because around which the aluminum of the casing is cast; and the conduit 424 extends inic communication with the conduit I3 where the latter is mounted in the lug 432. The central space 413 is connected with the bore 425 of a conduit 426 which extends into communication with the conduit 2l where the latter is secured within the lug 433. A valve member 421, comprising a cylindrical body portion 423 movable within the bore 4|5 in the plug member 4|4 and a tapered portion 423 adapted to coact with the outer end of the passage 4|1 in the plug member 4|4, controls the communication between the bores 423 and 425. The cylindrical portion 423 of the valve 421 is not a close fit for the bore 4|5, and cabin pressure, which has access to the space surrounding the stem portion of the valve member 421 as later described, enters the left-hand chamber 4|3 in Fig. 37 and flows, when the valve 421 is seated, through the annular groove 42|, the passage 422. the bore 423 of the conduit 424, and the conduit la, i'nto the bellows m. when the valve 421 is moved to the left and opens communication between the left-hand passage 4|1 and the leithand chamber 4|6, pressure may be transmitted from the conduit 424 through the passage 422,

75 radial passage 423, left-hand chamber 4|3, left- 

